WO2015086107A1 - Dispositif de soupape - Google Patents

Dispositif de soupape Download PDF

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Publication number
WO2015086107A1
WO2015086107A1 PCT/EP2014/003070 EP2014003070W WO2015086107A1 WO 2015086107 A1 WO2015086107 A1 WO 2015086107A1 EP 2014003070 W EP2014003070 W EP 2014003070W WO 2015086107 A1 WO2015086107 A1 WO 2015086107A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
piston
fluid
conical
rod
Prior art date
Application number
PCT/EP2014/003070
Other languages
German (de)
English (en)
Inventor
Frank Schulz
Michael Reik
Philipp Hilzendegen
Original Assignee
Hydac Fluidtechnik Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydac Fluidtechnik Gmbh filed Critical Hydac Fluidtechnik Gmbh
Priority to EP14803045.5A priority Critical patent/EP3080461B1/fr
Priority to US15/024,055 priority patent/US9869400B2/en
Publication of WO2015086107A1 publication Critical patent/WO2015086107A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
    • F16K11/105—Three-way check or safety valves with two or more closure members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/028—Shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • F16K15/026—Check valves with guided rigid valve members the valve being loaded by a spring the valve member being a movable body around which the medium flows when the valve is open
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1221—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1225—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston with a plurality of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3052—Shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/785—Compensation of the difference in flow rate in closed fluid circuits using differential actuators
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2564—Plural inflows
    • Y10T137/2567—Alternate or successive inflows
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2564—Plural inflows
    • Y10T137/2567—Alternate or successive inflows
    • Y10T137/2569—Control by depletion of source

Definitions

  • the invention relates to a valve device, in particular a releasable double check valve, preferably in the manner of a shuttle valve, with at least three fluid ports provided on a valve housing, at least two valve elements movable in the valve housing and at least one control device for driving the respective valve elements.
  • Valve devices of this type are state of the art. Such valve devices are used as shuttle valves in hydraulic and pneumatic circuits in which a logical OR
  • Shuttle valves have two inlet ports and one outlet port on the valve body.
  • the shuttle valve has two defined switching positions. In each switching position, one input port is always blocked by the associated valve element and the other input port is released so that fluid can pass from the released fluid port to the output port.
  • the respective valve element releases the higher pressure input port, while the other low pressure port is closed.
  • the respective valve element blocks the input connection leading to the higher pressure, while EP2014 / 003070
  • the lower pressure leading fluid port is open to the exit port.
  • a double-check valve designed as a shuttle valve, which has two valve elements, which are each assigned to an input port forming a fluid port 1 and fluid port 2, a control device in the form of a connecting element between the valve tilelementen is present, the valve elements in their movements between unlocking and Closing positions coupled with each other.
  • the valve elements are formed in the prior art by switching balls, so that each check valve is formed by a ball valve.
  • the invention has the object to provide a valve assembly of the said type available, which is characterized by a particularly favorable performance.
  • a valve device having the features of claim 1 in its entirety.
  • a significant feature of the invention is that at least one of the valve elements with parts of the valve housing forms a seat-tight closure part for the associated fluid connection point.
  • the replacement of the ball of a conventional ball valve by a cooperating with associated housing parts, seat-tight closure member avoids the problems associated with the prior art associated problems.
  • the formation of the respective valve element by a seat-tight closure part allows the realization of a shuttle valve, in which all connections are leak-free in the non-actuated switching position, in particular a positively covered valve arrangement can be realized.
  • the control device in contrast to the prior art, in which the valve elements of the double check valve are coupled together by a connecting member of the control device in their movements, the control device is designed such that it allows independent control of the valve elements.
  • the serious disadvantage of the conventional valve arrangements is avoided in the case of a respective unlocking process where all three connections are briefly connected to one another for a short time.
  • the switching process can be designed in such a way that the valve element, which is assigned to the fluid connection to be opened, carries out its opening movement independently of the other valve element remaining in the closed position.
  • control device can have a rod-like control element which is displaceable in the valve housing along the direction of travel of the valve elements and whose displacement in one or the other direction of travel allows the one or the other valve element to be entrained independently of the respective other valve element.
  • valve elements in the form of conical pistons are provided with a conical sealing surface which forms a seat-tight closure in cooperation with an associated sealing edge of the valve housing.
  • the design in the manner of valve cones a completely leak-free closure can be realized.
  • the arrangement can be made with particular advantage so that the cone pistons are biased by an energy storage device, preferably by a respective spring, in a closed position, in which a cone piston 3070
  • a first fluid connection assigned to it and the other conical piston sealing off a second fluid connection assigned to it in each case against a third fluid connection in each case without leakage, which adjoins both sealing edges.
  • the rod-like control member on each other opposed effective piston surfaces one of which can be acted upon by the pressure of the first fluid port and the second with the pressure of the second fluid port.
  • the switching movements of the conical pistons serving as valve elements are thus effected not by direct pressure actuation from the associated fluid connection, but rather by mechanical control by means of the rod-like control element which is moved by pressurizing its piston surfaces.
  • valve device is designed as a standard change-over valve
  • the effective piston surfaces of the rod-like control member are connected to the fluid port 1 and the fluid port 2 such that the control member is moved in one direction by the pressure of the respective higher pressure fluid port it moves the associated circuit the Fluidan ⁇ higher pressure poppet from the closed position and leaves the corresponding fluid port of the low pressure poppet in the closed position.
  • the arrangement when formed as an inverse control valve, can be made such that the effective piston surfaces of the rod-like control member are connected to the fluid connections in such a way that the rod-like control member is moved in a direction by the pressure of the respective higher pressure leading fluid connection, in which it moves the conical piston associated with the fluid connection of the lower pressure from the closed position and leaves the cone piston associated with the fluid connection of the higher pressure in the closed position.
  • control member in the form of a round rod, which passes through both conical pistons coaxially, wherein extending from the end-side piston surfaces, extending along the axis of travel bores in the rod channels for the fluid connection of the piston surfaces with the respectively associated fluid port Form 1 or 2.
  • a predetermined idle stroke of the control member can be provided for the entrainment of the conical piston by the rod-like control member.
  • the effective piston surfaces of the rod-like control member may have differently sized effective piston surfaces.
  • the arrangement can advantageously be made such that each conical piston has a piston surface which, when acted upon by the pressure of the respectively associated fluid connection, amplifies the spring force acting on the conical piston.
  • the leak-free seat-tight closure is favored by the correspondingly increased sealing force.
  • the conical shape of the conical pistons below the seat can positively influence the opening behavior via the stroke, eg in the sense of a damped opening.
  • valve concept according to the invention not only the described seat tightness is guaranteed, but at the same time a positively covered valve concept is realized, ie during the switching of the valve together with associated valve elements there is no fluid connection between at least two of the at least three fluid connections of the valve housing. Due to the positive overlap, the aforementioned connections can be switched independently of one another and attenuated accordingly as described above.
  • the mentioned seat tightness also results in an improved energy efficiency in the operation of the valve device. It has proved to be particularly advantageous to use the solution according to the invention for an inversely operating valve in the manner described above.
  • Fig. 1 in symbol representation, the hydraulic circuit of an application example of shuttle valves
  • Fig. 2 shows a comparison with a practical embodiment enlarged and schematically simplified drawn longitudinal section of an embodiment of the valve device according to the invention in the form of an inverse shuttle valve forming double check valve
  • Fig. 3 is a longitudinal section corresponding to Figure 2 of an alternative embodiment of the invention in the form of a standard shuttle valve
  • Fig. 4 and 5 corresponding longitudinal sections of two further embodiments of the invention in the form of inverse shuttle valves.
  • FIG. 1 shows by way of example the use of a standard shuttle valve 11 in a closed hydraulic circuit 13 for controlling a working cylinder 15.
  • the hydraulic circuit 13 has an electric motor-driven hydraulic pump 17 which, depending on the driving direction of rotation, in a first Line 19 or a second line 21 hydraulic pressure builds up.
  • a fluid connection 7 as an input connection to the line 19
  • a fluid connection 8 as a second input connection to the line 21 are connected.
  • the fluid connection 9 is connected as an outlet connection both with an openable check valve 23 and with an openable check valve 25.
  • the check valves 23, 25 each have an input port 27 and 29, which are connected to the line 19 and the line 21.
  • the respective input port 27, 29 is against the closing force of a respective spring 31 and 33 by the pressure signal at the fluid port 3 of the shuttle valve 1 1 unlocked to an output port 35 and 37 of the check valves 23, 25 with the piston chamber 39 or the rod space 41 of the working cylinder 1 5 to connect.
  • both the working cylinder 1 5 supplying check valves 23 and 25 from the fluid port 9 of the shuttle valve 1 1 forth unlocked, regardless of which of the lines 19 or 21, depending on the direction of rotation of the pump 1 7, the pressure line or return line, so that by selecting the drive of the pump 1 7, the activity of the working cylinder 15 is controllable.
  • FIG. 2 shows a first exemplary embodiment of the invention
  • Valve device in the form of a double check valve, which forms an inverse shuttle valve.
  • the associated valve housing 51 has an inner working space which extends in the form of a stepped bore along an actuating travel axis.
  • the work space formed by the steps formed is divided into sections of different diameters, of which a fluid space 53 offset to the left from the central area is in communication with the fluid port 1 as the inlet port of the housing 51.
  • a fluid space 55 offset to the right from the central area communicates with the fluid port 2 as a second input port of the housing 51, and an intermediate third fluid space 57 communicates with the fluid port 3 as the output port of the housing 51.
  • the middle fluid space 57 has a smaller diameter than the other fluid spaces 53, 55.
  • the step of the valve housing 51 which is thus located at the transition to the adjoining fluid space 53 and 55, respectively forms a sealing edge 59 and 61 for forming a seat-tight closure in cooperation with a conical surface 63, which is designed as a sealing surface on an associated conical piston.
  • a first conical piston 65 is designated, which is assigned to the first fluid space 53 connected to the fluid connection 1, and a second conical piston 67, which is assigned to the fluid space 55, which is in communication with the fluid connection 2.
  • valve elements of a double check valve forming conical piston 65, 67 are biased by a respective compression spring 69, which are supported on the conical surface 63 opposite surface of the conical piston 65, 67 in the closed position shown in Figure 2.
  • a control device is provided with a control member movable along the travel axis. This is formed by a round bar 71, which is movably guided in the housing 51, and each end has a piston surface 73 and 75 which can be acted upon by fluid.
  • the rod 71 passes through the conical pistons 65, 67 coaxially, these forming a relative movement of the rod 71 permitting inner guide, which is sealed at each cone piston 65, 67 by a respective sealing member 77.
  • the rod 71 has a driver device, formed by two radial projections 79, one of which is located in the vicinity of an adjacent conical piston 65, 67.
  • one or the other conical piston 65 or 67 is taken after a small idle stroke, which is determined by the size of the distance of the projections 79 from the adjacent conical piston 65, 67, and against the effect the respective associated compression spring 69 lifted from the sealing edge 59 or 61 to connect the fluid port 1 or the fluid port 2 with the fluid port 3 as administratansehl uss.
  • a small idle stroke which is determined by the size of the distance of the projections 79 from the adjacent conical piston 65, 67, and against the effect the respective associated compression spring 69 lifted from the sealing edge 59 or 61 to connect the fluid port 1 or the fluid port 2 with the fluid port 3 as Nathanansehl uss.
  • an oblique bore 81 is formed which leads to the space surrounding the compression spring 69.
  • a further connecting channels to the piston surface 73 are in the rod 71, starting from the end, along the axis of travel extending bore 83 formed with a transverse bore 85.
  • the other conical piston 67 likewise has a helical bore 81 around the piston surface 75 located at the right-hand end of the rod 71 via a longitudinal bore 83 and a transverse bore 85 of the rod 71 to supply with the pressure of the fluid port 2.
  • the rod 71 moves in Figure 2 to the left for a corresponding entrainment of the conical piston 65 from the closed position, so that the fluid port 1 is unlocked.
  • the conical piston 65 or 67 not entrained by the movements of the rod 71 remains in the closed position.
  • FIG. 3 which is designed as a standard shuttle valve, differs from the example of Figure 2 only by a different type of training in the rod 71 extending channels for connecting the piston surfaces 73 and 75 with the fluid ports 1 and 2
  • the rod 71 starting from each piston surface 73 and 75, respectively has a longitudinal bore 87 and 89 which run parallel to each other, and of which the longitudinal bore 87, the piston surface 73 via a transverse bore 91 with the space surrounding the spring 69 of the conical piston 67 connects, while the other longitudinal bore 89 connects the piston surface 75 via a transverse bore 91 with the space surrounding the spring 69 of the conical piston 65.
  • the rod 71 starting from each piston surface 73 and 75, respectively has a longitudinal bore 87 and 89 which run parallel to each other, and of which the longitudinal bore 87, the piston surface 73 via a transverse bore 91 with the space surrounding the spring 69 of the conical piston 67 connects, while the other longitudinal bore 89 connects the piston surface 75 via a trans
  • the mode of operation corresponds to the example of FIG. 2, wherein throttling points can likewise be formed in the oblique bores 81.
  • throttling points can likewise be formed in the oblique bores 81.
  • the seal is not made by sealing elements 77 between the conical piston 65, 67 and housing 51, but by means of sealing elements 78 between the rod 71 and the housing 51.
  • throttling may be provided through an orifice in line 93 and / or 95.
  • Drawing right-side end portion of a rod portion 99 is provided with an enlarged diameter.
  • the piston surface 75 has a larger effective area than the piston surface 73 of the other end. Can be characterized on the choice of the sizes of piston surfaces 73, 75 to adjust the switching behavior to respective anassemblesspe ⁇ -specific requirements.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif de soupape, en particulier une soupape anti-retour double déblocable, de préférence du type distributeur, comportant au moins trois raccords de fluide (1, 2, 3) prévus dans un corps de soupape (51) ; au moins deux éléments de soupape (65, 67) mobiles en translation dans le corps de soupape (51) ainsi qu'au moins un dispositif de commande (71) destiné à commander les éléments de soupape individuels (65, 67). Le dispositif est caractérisé en ce qu'au moins l'un des éléments de soupape (65, 67) forme avec des parties (59/61) du corps de soupape (51) un élément obturateur à appui étanche pour les raccords de fluide (1, 2, 3) correspondants.
PCT/EP2014/003070 2013-12-13 2014-11-18 Dispositif de soupape WO2015086107A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP14803045.5A EP3080461B1 (fr) 2013-12-13 2014-11-18 Valve
US15/024,055 US9869400B2 (en) 2013-12-13 2014-11-18 Valve device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013020585.9A DE102013020585A1 (de) 2013-12-13 2013-12-13 Ventilvorrichtung
DE102013020585.9 2013-12-13

Publications (1)

Publication Number Publication Date
WO2015086107A1 true WO2015086107A1 (fr) 2015-06-18

Family

ID=51987112

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/003070 WO2015086107A1 (fr) 2013-12-13 2014-11-18 Dispositif de soupape

Country Status (4)

Country Link
US (1) US9869400B2 (fr)
EP (1) EP3080461B1 (fr)
DE (1) DE102013020585A1 (fr)
WO (1) WO2015086107A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3360782A1 (fr) * 2017-02-09 2018-08-15 Goodrich Corporation Soupape énergétique de terminaison séquencielle à usage unique

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US10670155B2 (en) * 2015-10-05 2020-06-02 Proserv Gilmore Valve Llc Latching poppet valve
DE102016113294A1 (de) * 2016-07-19 2018-01-25 Dorst Technologies Gmbh & Co. Kg Hydraulische Antriebseinrichtung
US10591076B2 (en) 2016-09-15 2020-03-17 Proserv Operations, Inc. Low friction hydraulic circuit control components
DE102017002062A1 (de) 2017-03-03 2018-09-06 Wabco Gmbh Doppelrückschlagventil einer Luftaufbereitungseinheit
US10739796B2 (en) 2017-09-22 2020-08-11 Proserv Gilmore Valve Llc Pressure regulator with reconfigurable hydraulic dampening
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CN108019535B (zh) * 2018-01-04 2023-11-24 中国石油大学(北京) 阀芯采用密封锥面的两位三通换向阀
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US9869400B2 (en) 2018-01-16
EP3080461A1 (fr) 2016-10-19
EP3080461B1 (fr) 2018-12-12
US20160230900A1 (en) 2016-08-11
DE102013020585A1 (de) 2015-06-18

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